Combined power system

ABSTRACT

For a rotary electric machine housing, a cooling jacket and compressed air flow passages are formed on an outer circumferential side of the cooling jacket. On an outer side wall of the rotary electric machine housing, a terminal casing is formed and electric terminal portions are accommodated in the terminal casing. Air bleed ports are formed in a shroud case of a gas turbine engine. Compressed air that is compressed by a compressor wheel flows into the air bleed ports. The compressed air that has passed through the air bleed ports flows through air bleed passages formed in an engine housing and the compressed air flow passages. Then, the compressed air reaches the terminal casing.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is based upon and claims the benefit of priority fromJapanese Patent Application No. 2021-062130 filed on Mar. 31, 2021, thecontents of which are incorporated herein by reference.

BACKGROUND OF THE INVENTION Field of the Invention

The present invention relates to a combined power system integrallyconstituted by a rotary electric machine and a gas turbine engine.

Description of the Related Art

In JP 2005-106029 A, a combined power system is disclosed in which arotary electric machine and a gas turbine engine, which is one type ofinternal combustion engine, are combined together and integrated. Inthis case, a rotating shaft of the rotor constituting the rotaryelectric machine and an output shaft of the gas turbine engine areconnected on the same axial line, and both shafts thereof rotatetogether integrally. In this instance, as shown respectively in FIG. 1of JP 2005-106029 A and FIG. 1 of JP 2016-174443 A, the rotating shaftis capable of being rotatably supported via a journal (bearing) withrespect to a rotary electric machine housing in which a stator isaccommodated.

As shown in JP 2016-174443 A, in the rotary electric machine housing, aconnector is provided for electrically connecting the rotary electricmachine and an external device to and from which electrical power istransmitted and received. When an electrical current flows through anelectromagnetic coil or the electric terminal portions inside aconnector, such elements become heated. Due to such heat, the conversionefficiency from electrical energy to thermal energy, or vice versa, isreduced. In JP 2016-174443 A and JP 2016-059133 A, a cooling structureis proposed for avoiding such an inconvenience.

SUMMARY OF THE INVENTION

Compressed air is generated by the gas turbine engine. In the combinedpower system, it is considered that the compressed air is used as acooling air for cooling an electric terminal portion. In this case, thisis because there is an advantage in that a compressed air supply sourceor the like becomes unnecessary. However, since the temperature of thecompressed air generated by the gas turbine engine is relatively high,it is difficult to use it as a cooling air.

A principal object of the present invention is to provide a combinedpower system that is capable of cooling an electric terminal portionwithout providing a compressed air supply source or cooling equipment.

Another object of the present invention is to provide a combined powersystem in which full conversion efficiency is achieved, from electricalenergy to thermal energy, or vice versa.

According to an aspect of the present invention, a combined power systemis provided. The combined power system includes:

a rotary electric machine system including a rotary electric machine,and a rotary electric machine housing in which a rotating shaft of therotary electric machine is rotatably supported; and

a gas turbine engine including an output shaft configured to support aturbine wheel and a compressor wheel and rotate integrally with therotating shaft, and an engine housing in which the turbine wheel and thecompressor wheel are accommodated,

the combined power system further including a terminal casing disposedon an outer side wall of the rotary electric machine housing and inwhich electric terminal portions are accommodated, the electric terminalportions being configured to transmit and receive electrical powerbetween the rotary electric machine and an external device,

wherein an air bleed port is formed in a shroud case that surrounds thecompressor wheel, and compressed air that is compressed by thecompressor wheel flows into the air bleed port,

an air bleed passage is formed in the engine housing, and the compressedair that has passed through the air bleed port flows through the airbleed passage,

a cooling jacket is provided for the rotary electric machine housing, acompressed air flow passage is formed on an outer circumferential sideof the cooling jacket, and the compressed air that has flowed throughthe air bleed passage flows through the compressed air flow passage, and

the terminal casing is disposed on a downstream side of the compressedair flow passage.

According to the present invention, the cooling jacket is provided forthe rotary electric machine housing, and a compressed air flow passageis formed on an outer circumferential side of the cooling jacket. Thecompressed air is generated by the gas turbine engine and flows alongthe air bleed passage. The heat of the compressed air is conducted tothe cooling medium in the cooling jacket when the compressed air flowsthrough the compressed air flow passage. As a result, the temperature ofthe compressed air becomes comparatively low. The compressed air whosetemperature has been thus lowered can sufficiently cool the electricterminal portion.

Therefore, without an additional compressed air supply source or coolingequipment, full conversion efficiency is achieved, from electricalenergy to thermal energy, or vice versa. Moreover, since there is noneed to separately provide a compressed air supply source or coolingequipment, it is possible to reduce the size and scale of a combinedpower system.

The above and other objects, features, and advantages of the presentinvention will become more apparent from the following description whentaken in conjunction with the accompanying drawings, in which apreferred embodiment of the present invention is shown by way ofillustrative example.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic overall perspective view of a combined powersystem according to an embodiment of the present invention;

FIG. 2 is a schematic overall perspective view of a rotary electricmachine system constituting part of the combined power system;

FIG. 3 is a schematic side cross-sectional view of the rotary electricmachine system;

FIG. 4 is an enlarged view of principal components shown in FIG. 3 ;

FIG. 5 is an enlarged view of principal components shown in FIG. 3 , ata location that differs from that shown in FIG. 4 ;

FIG. 6 is a schematic perspective view of a second sub-housingconstituting a rotary electric machine housing, and an inner housingconstituting an engine housing;

FIG. 7 is a schematic configuration diagram of an electrical currentconverter provided in the rotary electric machine housing;

FIG. 8 is a schematic side cross-sectional view of a gas turbine engineconstituting part of the combined power system; and

FIG. 9 is an enlarged view of principal components shown in FIG. 8 .

DESCRIPTION OF THE INVENTION

A preferred embodiment of a combined power system according to thepresent invention will be presented and described in detail below withreference to the accompanying drawings. In should be noted that, in thefollowing description, although the terms “left,” “right,” “down,” and“up” designate the leftward, rightward, downward, and upward directionsshown in FIGS. 3 to 5, 8 and 9 , such a designation is merely for thesake of convenience in order to facilitate understanding, and theposture when the combined power system is actually placed in use is notlimited.

FIG. 1 is a schematic overall perspective view of a combined powersystem 300 according to an embodiment of the present invention. Thecombined power system 300 comprises a rotary electric machine system 10and a gas turbine engine 200 which is an internal combustion engine. Thegas turbine engine 200 is disposed on a right side in an axial directionof the rotary electric machine system 10. Further, an axis that extendsalong a longitudinal direction (axial direction) and passes through adiametrical center of the rotary electric machine system 10, and an axisthat extends along a longitudinal direction (axial direction) and passesthrough a diametrical center of the gas turbine engine 200 coincide witheach other.

Stated otherwise, the rotary electric machine system 10 and the gasturbine engine 200 are arranged in parallel on the same axis. Thecombined power system 300 which is configured in such a manner can beused, for example, as a power source for propulsion in a flying objectsuch as a drone, or in a ship, an automobile, or the like.Alternatively, the combined power system 300 can be used as a powersource for an auxiliary power source in an aircraft, a ship, a building,or the like. When mounted on a flying body such as a multicopter or thelike, the combined power system 300 functions as a power drive source torotationally energize a motor constituting a lift generating device suchas a prop, a ducted fan, or the like. Further, when mounted on a ship,the combined power system 300 functions as a rotational force generatingdevice for a screw, and when mounted on an automobile, the combinedpower system 300 functions as a power drive source for rotationallyurging a motor that constitutes an engine. In addition, the combinedpower system 300 can be applied to gas turbine electrical powergenerating facilities. Moreover, in the present embodiment, as will bedescribed later, the gas turbine engine 200 serves in a dual manner as agas supply source for supplying compressed air (gas).

First, a description will be given concerning the rotary electricmachine system 10. FIG. 2 and FIG. 3 are, respectively, a schematicoverall perspective view and a schematic side cross-sectional view ofthe rotary electric machine system 10. The rotary electric machinesystem 10 comprises a rotary electric machine 12 (for example, anelectrical power generator) and a rotary electric machine housing 14 inwhich the rotary electric machine 12 is accommodated. The rotaryelectric machine housing 14 exhibits a substantially cylindrical shape,and includes a main housing 16 that has open ends on both the left andright ends thereof, a first sub-housing 18 connected to the left end ofthe main housing 16, and a second sub-housing 20 connected to the rightend of the main housing 16.

The main housing 16 has a substantially cylindrical shape in which athick side wall extends along a lateral (left-right) direction. Acooling jacket 21 through which a cooling medium flows is formed in theinner portion of the side wall. As a specific example of the coolingmedium, there may be cited cooling water, and in this case, the coolingjacket 21 is a water jacket. Further, on an outer surface (an outer sidewall) of the side wall of the main housing 16, in the vicinity of a leftend thereof, a terminal casing 22 and a measuring device casing 24 aredisposed integrally with the main housing 16.

Furthermore, on an outer side wall of the main housing 16, there areprovided hollow pipe members 158 a to 158 c that extend along alongitudinal direction (the left-right direction in FIG. 3 ) of the mainhousing 16. The hollow interior parts of the hollow pipe members 158 ato 158 c are compressed air flow passages through which a curtain airflows. Further, a detector retaining member that retains the rotationparameter detector is connected to the first sub-housing 18. Accordingto the present embodiment, the rotation parameter detector isexemplified by a resolver 140. Accordingly, hereinafter, the detectorholding member that is connected to the first sub-housing 18 will bereferred to as a “resolver holder 26”. A cap cover 28 is screw-engagedwith the resolver holder 26. Concerning the above-described elements, adetailed description thereof will be provided later.

The rotary electric machine 12 includes a rotor 30, and a stator 32 thatsurrounds an outer circumferential side of the rotor 30.

The rotor 30 includes a rotating shaft 40 configured such that an innerside shaft 34 is capable of being removably inserted into a hollowcylindrical outer side shaft 36. More specifically, the outer side shaft36 is a hollow body having a substantially cylindrical shape, and bothends of which are open ends. That is, the outer side shaft 36 includes aleft opening end 42 a (see FIG. 4 ) and a right opening end 42 b (seeFIG. 5 ).

On the other hand, the inner side shaft 34 is longer in length than theouter side shaft 36. The inner side shaft 34 includes a cylindricalcolumn portion 44 a diameter of which is minimal, a left end part 46 a(see FIG. 4 ) which is connected to a left side of the cylindricalcolumn portion 44 and a diameter of which is larger in comparison withthe cylindrical column portion 44, and a right end part 46 b (see FIG. 5) which is connected to the right side of the cylindrical column portion44 and a diameter of which is larger in comparison with the cylindricalcolumn portion 44 and smaller in comparison with the left end part 46 a.Among these elements, one portion of the left end part 46 a projects outand is exposed from the left opening end 42 a of the outer side shaft36, and becomes a protruding distal end 104 to be described later.Moreover, although in the illustrated example, the right end part 46 band the right opening end 42 b of the outer side shaft 36 are flush witheach other, the right end part 46 b may be at a position that isslightly recessed from the right opening end 42 b.

As shown in detail in FIG. 4 , on the left end part 46 a of the innerside shaft 34, there are provided in this order from the left toward theright a first external threaded portion 48, a flange portion 50, astopper portion 52, and a second external threaded portion 54. The outerdiameters of the first external threaded portion 48, the flange portion50, the stopper portion 52, and the second external threaded portion 54become larger in this order. The outer diameter of the second externalthreaded portion 54 is set to be larger than the inner diameter of theouter side shaft 36, and therefore, the right end of the second externalthreaded portion 54 is held back by the edge of the left opening end 42a of the outer side shaft 36. Consequently, part of the inner side shaft34 on a leftward side of the second external threaded portion 54 isprevented from being inserted inside the outer side shaft 36.

A resolver rotor 56 is mounted on the flange portion 50, together with asmall cap nut 58 being screwed-engaged with the first external threadedportion 48. The resolver rotor 56 is positioned and fixed to the flangeportion 50 by the right end thereof end being held back by the stopperportion 52, together with the left end being pressed by the small capnut 58. Further, a large cap nut 60 is screwed-engaged with the secondexternal threaded portion 54. A skirt portion 61 of the large cap nut 60covers the outer circumferential wall of the left opening end 42 a ofthe outer side shaft 36. Consequently, the left end part 46 a of theinner side shaft 34 is constrained by the left opening end 42 a of theouter side shaft 36. Both the first external threaded portion 48 and thesecond external threaded portion 54 are so-called reverse threads.Accordingly, the small cap nut 58 and the large cap nut 60 are rotatedcounterclockwise at a time of being screw-engaged. Further, by portionsof the threads of the small cap nut 58 and the large cap nut 60 beingdeformed, it is possible to prevent the small cap nut 58 and the largecap nut 60 from being loosened any more than at the time ofscrew-engagement thereof.

As shown in FIG. 5 , a shaft connecting hole 62 is formed in the rightend part 46 b of the inner side shaft 34 in a manner so as to extendtoward a left end part 46 a side. A female threaded portion 64 isengraved on an inner circumferential wall of the shaft connecting hole62. Further, a first inner circumferential side spline 66 (innercircumferential side engaging portion) that extends along the left-rightdirection is formed on an outer circumferential wall of the rightopening end 42 b of the outer side shaft 36.

The second sub-housing 20, which exhibits a substantially disk shape, isconnected via non-illustrated bolts to the main housing 16. A center ofthe second sub-housing 20 forms a thick-walled cylindrical portion, anda large-diameter insertion hole 68 is formed in such a cylindricalportion. A second bearing 94 (described later) is inserted into theinsertion hole 68. The second bearing 94 is sandwiched between and ispositioned and fixed by an inner stopper 70 and an outer stopper 71.

As shown in FIG. 2 , an annular recessed portion 72 is formed in an endsurface of the second sub-housing 20 in facing relation to the gasturbine engine 200, together with an annular collection flow path 74being formed in the annular recessed portion 72. As will be describedlater, a portion of the compressed air generated by the gas turbineengine 200 is diverted into and flows through the collection flow path74. Upstream side communication holes 76 are formed at three locationson a bottom wall of the annular recessed portion 72.

Further, as shown in FIG. 6 , relay communication passages 78 areprovided in an interior part of the second sub-housing 20. The relaycommunication passages 78 extend in a radial form along a diametricaldirection of the second sub-housing 20, together with communicating in adiametrically outward direction with the collection flow path 74 via theupstream side communication holes 76 externally in the diametricaldirection. Furthermore, three downstream side communication holes 80 ato 80 c are formed on an end surface of the second sub-housing 20 infacing relation to the rotary electric machine 12. The downstream sidecommunication holes 80 a to 80 c are downstream side openings of therelay communication passages 78. The three downstream side communicationholes 80 a to 80 c individually open into each of the hollow pipemembers 158 a to 158 c. As can be understood from such a configuration,the relay communication passages 78 place the collection flow path 74 incommunication with the hollow interior parts (compressed air flowpassages) of the hollow pipe members 158 a to 158 c. A distributionpassage is formed by the collection flow path 74 and the relaycommunication passages 78.

As shown in FIG. 5 , a rectifying member 82 is provided on an endsurface (on one end part in the axial direction) of the secondsub-housing 20 on a side facing toward the gas turbine engine 200, in amanner so as to project toward a gas turbine engine 200 side. Therectifying member 82 is made up from a chevron shaped body or abottomless cup-shaped body, in which a base portion thereof facingtoward a side of the second sub-housing 20 is formed in a large diameterand thin-walled annular shape, and a top portion thereof facing towardthe gas turbine engine 200 is formed in a small diameter andthick-walled annular shape. In addition, a side circumferential wall 83between the base portion and the top portion is a smooth surface with asmall amount of surface roughness.

Further, a diameter (opening diameter) of a through hole 84 on a topportion side is set to be greater than an outer diameter of the outerstopper 71. Therefore, a right end of the outer stopper 71 which hasentered into the through hole 84 does not interfere with an inner wallof the through hole 84. Stated otherwise, a gap is formed between anouter circumferential wall of the outer stopper 71 and the inner wall ofthe through hole 84.

A left end of an output shaft 250 is inserted into the shaft connectinghole 62 that is formed in the inner side shaft 34. The output shaft 250is coupled to the inner side shaft 34 by means of screw-engagement, aswill be described later. Moreover, the output shaft 250 supports acompressor wheel 230 and a turbine wheel 232 that constitute the gasturbine engine 200 (see FIG. 8 ).

As shown in FIG. 3 , an outer diameter of a substantially intermediateportion in a longitudinal direction of the outer side shaft 36 is set tobe a maximum diameter, and a plurality of permanent magnets 88 areretained by a magnet holder 90 on such a large diameter portion. Theadjacent permanent magnets 88 themselves are arranged adjacent to eachother, and the adjacent magnets have polarities different from eachother facing toward the outer circumferential side. Accompanyingrotation of the rotating shaft 40, the individual permanent magnets 88revolve about a center of rotation of the rotating shaft 40.

A left end (first end part) of the rotating shaft 40 is rotatablysupported in the first sub-housing 18 via a first bearing 92. Further, aright end (second end part) of the rotating shaft 40 is rotatablysupported in the second sub-housing 20 via the second bearing 94. Inthis instance, as shown in FIG. 3 , according to the present embodiment,the first bearing 92 is interposed between the outer side shaft 36 andthe first sub-housing 18. Further, the second bearing 94 is interposedvia the inner stopper 70 between the outer side shaft 36 and the secondsub-housing 20.

More specifically, the first sub-housing 18 includes a columnarprotrusion 96 that protrudes toward the main housing 16 and exhibits asubstantially cylindrical shape, and a first shaft insertion hole 98 isformed in such a columnar protrusion 96. The first bearing 92 isdisposed inside the first shaft insertion hole 98.

A leftward opening of the first shaft insertion hole 98 is closed by adisk-shaped member 102 in which a second shaft insertion hole 100connected to the first shaft insertion hole 98 is formed. Althoughdetailed illustration thereof is omitted, an outer circumferential wallof the left opening end 42 a of the outer side shaft 36 and therespective inner circumferential walls of the first shaft insertion hole98 and the second shaft insertion hole 100 are slightly separated awayfrom each other. Further, the skirt portion 61 of the large cap nut 60is slightly separated away from the left end surface of the disk-shapedmember 102.

A distal end of the left end part of the rotating shaft 40 is passedthrough an inner hole of the first bearing 92, is passed through thefirst shaft insertion hole 98 and the second shaft insertion hole 100,and is exposed in a protruding manner to the exterior of the firstsub-housing 18. Hereinafter, a portion of the rotating shaft 40 thatprotrudes from the left end of the first bearing 92 is referred to as aprotruding distal end, and is designated by the reference numeral 104.On the protruding distal end 104, within the left end part 46 a of theinner side shaft 34, there are included the first external threadedportion 48, the flange portion 50, the stopper portion 52, and thesecond external threaded portion 54 (see FIG. 4 ). On the other hand,the right end of the rotating shaft 40 is passed through the inner holeof the second bearing 94, and protrudes together with the outer stopper71 from the insertion hole 68 that is formed in the second sub-housing20 (see FIG. 5 ).

As shown in FIG. 3 , the first shaft insertion hole 98 and aflow-through hole 106 formed in the inner stopper 70 communicate with anaccommodation chamber 114 (to be described later) which is an internalspace of the main housing 16. Therefore, the first bearing 92 and thesecond bearing 94 are exposed in the accommodation chamber 114. Itshould be noted, of course, that the second shaft insertion hole 100communicates with the accommodation chamber 114 via the first shaftinsertion hole 98.

In the present embodiment, the first bearing 92 and the second bearing94 are so-called jet lubrication type bearings, which are lubricated andcooled by the lubricating oil that is supplied in the form of a jetflow. The type of the bearings is not particularly limited to thisfeature, and the bearings may be of a circulation lubrication type, or aspray lubrication type in which an oil mist is sprayed thereon.Lubricated bearings of this type are well known, and accordingly,detailed illustration and description thereof will be omitted.

The stator 32 that constitutes the rotary electric machine 12 togetherwith the above-described rotor 30 includes an electromagnetic coil 116,and a plurality of insulating base members 118 around which theelectromagnetic coil 116 is wound. Among these elements, theelectromagnetic coil 116 includes three types, namely, a U-phase coil, aV-phase coil, and a W-phase coil. More specifically, in the case thatthe rotary electric machine 12 is used as a generator, the rotaryelectric machine 12 is a so-called three-phase power supply. Moreover,the plurality of insulating base members 118 are arranged in an annularshape, whereby an inner hole is formed in the stator 32.

The stator 32 is accommodated in the accommodation chamber 114 that isformed in the main housing 16. In this instance, the second sub-housing20 fulfills a role as a stator holder. More specifically, the insulatingbase members 118 that constitute the stator 32 are engaged with anannular recessed portion 122 formed in the second sub-housing 20. Due tosuch engagement, the stator 32 is positioned and fixed in place.Furthermore, the columnar protrusion 96 enters into the inner hole ofthe stator 32 from the leftward opening thereof.

Although detailed illustration thereof is omitted, inner walls of theaccommodation chamber 114 and the electromagnetic coil 116 are slightlyseparated away from each other. Due to such separation, the main housing16 and the electromagnetic coil 116 are electrically isolated from eachother.

Moreover, by slightly separating both members away from each other,clearances are formed between the outer circumferential wall of thecolumnar protrusion 96 and the insulating base members 118, and betweenthe outer walls of the permanent magnets 88 and the inner wall of theelectromagnetic coil 116. As will be discussed later, these clearancesbecome a portion of the flow passage through which the curtain air,which is a gas, flows.

As shown in FIG. 4 , the first sub-housing 18 has an annular convexportion 124 that projects out in an annular shape. An inner side of theannular convex portion 124 is formed with a hollow recessed portion 126.The protruding distal end 104 constituting the left end part 46 a of theinner side shaft 34 is inserted into the hollow recessed portion 126.

The resolver holder 26 which retains a resolver stator 130 is providedon the annular convex portion 124. The resolver holder 26 includes aflange-shaped stopper 132 that protrudes outwardly in a diametricaldirection. The flange-shaped stopper 132 is set to have a greaterdiameter than the inner diameter of the annular convex portion 124, andaccordingly, the resolver holder 26 is positioned by the flange-shapedstopper 132 coming into abutment against the annular convex portion 124.In this state, the resolver holder 26 is connected to the firstsub-housing 18, for example, via a mounting bolt or the like (notshown).

On the resolver holder 26, at a boundary with the flange-shaped stopper132, there are provided a leftward facing small cylindrical portion 134,and a rightward facing large cylindrical portion 136 having a largerdiameter in comparison with the small cylindrical portion 134. Aretaining hole 138 is formed in the resolver holder 26, and the resolverstator 130 is retained by a right end thereof being fitted into theretaining hole 138. When the large cylindrical portion 136 enters intothe hollow recessed portion 126 together with the flange shaped stopper132 abutting against the annular convex portion 124, the resolver rotor56, which is retained by the flange portion 50 of the left end part 46 aof the inner side shaft 34, is positioned in the inner hole of theresolver stator 130. These elements including the resolver stator 130and the resolver rotor 56 constitute the resolver 140 which serves as arotation parameter detector. According to the present embodiment, a caseis exemplified in which an angle of rotation is detected by the resolver140.

A signal receiver connector 144 is fitted into a fitting hole 142 formedin the flange-shaped stopper 132. The resolver stator 130 and the signalreceiver connector 144 are electrically connected to each other via asignal line 146. A receiver-side connector of a signal receiver (notshown), which receives signals emitted by the resolver 140, is insertedonto the signal receiver connector 144. The resolver 140 and a signalreceiver are electrically connected via the signal receiver connector144 and the receiver-side connector.

A plurality of tab portions 148 (which are omitted from illustration inFIG. 1 ) are provided on the small cylindrical portion 134. One of suchtab portions is shown in FIG. 3 . Furthermore, the small cylindricalportion 134 is covered by the cap cover 28, which closes a leftwardopening of the small cylindrical portion 134 and shields the left endpart 46 a of the inner side shaft 34. The cap cover 28 is connected tothe tab portions 148 via connecting bolts 150.

As noted previously, the terminal casing 22 and the measuring devicecasing 24 are integrally provided on a side wall in close proximity tothe left end of the main housing 16. Among these elements, a thermistor152, which is a temperature measuring device, is accommodated in themeasuring device casing 24. Although not illustrated in particular,measurement terminals of the thermistor 152 are drawn out from themeasuring device casing 24 and are connected to the electromagnetic coil116. From the measuring device casing 24, a harness 154 which isconnected to the thermistor 152 is drawn out to the exterior.

In the terminal casing 22 which is adjacent to the measuring devicecasing 24, there are accommodated a U-phase terminal 156 a, a V-phaseterminal 156 b, and a W-phase terminal 156 c that are electricallyconnected to ends of a U-phase coil, a V-phase coil, and a W-phase coil.Stated otherwise, the terminal casing 22 is a connector for connectingan external device to which there is connected a battery 170 (refer toFIG. 7 ) that serves as an external power source that is electricallyconnected to the rotary electric machine 12, and the U-phase terminal156 a, the V-phase terminal 156 b, and the W-phase terminal 156 c areelectric terminal portions that supply electrical power to the battery170. Moreover, an internal space of the measuring device casing 24 andan internal space of the terminal casing 22 communicate with each otherthrough a non-illustrated casing-to-casing communication hole.

As shown in FIG. 2 , the hollow pipe members 158 a to 158 c, which areprovided on the outer surface of the side wall of the main housing 16,are positioned externally of the cooling jacket 21 that is formed in aninterior part of the side wall of the main housing 16. Morespecifically, the hollow pipe members 158 a to 158 c, for example, lieadjacent to the cooling jacket 21. In this instance, according to thepresent embodiment, although a case is illustrated in which three of thehollow pipe members 158 a to 158 c are provided, the number of thehollow pipe members depends on a required flow rate and a required flowvelocity of the curtain air. More specifically, the number of the hollowpipe members is not particularly limited to three. Further, in a similarmanner, the cross-sectional area of the hollow pipe members may beappropriately set according to the required flow rate and the requiredflow velocity of the curtain air.

In this instance, right ends of the hollow pipe members 158 a to 158 cindividually overlap with the three downstream side communication holes80 a to 80 c (see FIG. 6 ) that are formed in the second sub-housing 20.More specifically, the collection flow path 74 communicates with theinterior parts of the hollow pipe members 158 a to 158 c via theupstream side communication holes 76, the relay communication passages78, and the downstream side communication holes 80 a to 80 c. On theother hand, a left end of the hollow pipe member 158 a communicates witha hollow interior part of the measuring device casing 24, and left endsof the hollow pipe members 158 b and 158 c communicate with a hollowinterior part of the terminal casing 22.

The curtain air flows on an upstream side through the collection flowpath 74, and flows on a downstream side through the measuring devicecasing 24 and the terminal casing 22. In this manner, the hollow pipemembers 158 a to 158 c are portions of the compressed air flow passagesthrough which the curtain air flows. Moreover, the curtain air is aportion of the compressed air that is supplied from the gas turbineengine 200.

As shown in FIG. 3 , the internal space of the terminal casing 22communicates with the accommodation chamber 114. Therefore, the curtainair that has flowed into the internal space of the terminal casing 22 iscapable of flowing into the accommodation chamber 114 and coming intocontact with the first bearing 92 and the second bearing 94.

As shown in FIGS. 1 and 2 , an electrical current converter 172 isprovided on an outer circumferential wall of the main housing 16 at alocation closer to the gas turbine engine 200 than the terminal casing22 is. As shown in FIG. 7 , the electrical current converter 172includes a conversion circuit 174, a capacitor 176, and a controlcircuit 178. The conversion circuit 174, the capacitor 176, and thecontrol circuit 178 are accommodated inside an equipment case 180. Theequipment case 180, for example, is disposed on the outercircumferential wall of the main housing 16 at a location that does notinterfere with the hollow pipe members 158 a to 158 c (see FIG. 1 ).

The conversion circuit 174 is constituted to include a power module 182,which has a function of converting an alternating current generated inthe electromagnetic coil 116 into a direct current. Further, thecapacitor 176 temporarily stores as an electric charge the directcurrent converted by the conversion circuit 174. Moreover, theconversion circuit 174 also has a function of converting the directcurrent delivered thereto from the battery 170 into an alternatingcurrent. In this case, the capacitor 176 temporarily stores as anelectric charge the direct current delivered from the battery 170 towardthe electromagnetic coil 116. The control circuit 178 controls a currentdensity of the direct current from the capacitor 176 to the battery 170,or the direct current from the battery 170 to the capacitor 176. Thedirect current from the battery 170 is supplied to the motor, forexample, via an AC-DC converter (neither of which is shown).

As shown in FIG. 7 , in this case, the equipment case 180 is positionedand fixed so as to abut against the outer circumferential wall of themain housing 16. In addition, in the equipment case 180, the conversioncircuit 174 and the capacitor 176 are arranged so as to be in closeproximity to the main housing 16. Since the cooling jacket 21 isprovided in the main housing 16 as described above, the conversioncircuit 174 and the capacitor 176 are sufficiently close to the coolingjacket 21.

Next, the gas turbine engine 200 will be described. As shown in FIG. 8 ,the gas turbine engine 200 is equipped with an engine housing 206including an inner housing 202 connected to the second sub-housing 20 ofthe rotary electric machine system 10, and an outer housing 204connected to the inner housing 202.

As shown in FIGS. 1 and 6 , the inner housing 202 includes a firstannular portion 208 connected to the second sub-housing 20, a secondannular portion 210 having a maximal diameter, and a plurality of (forexample, six) leg members 212 connecting the first annular portion 208and the second annular portion 210. Further, a cylindrical cover member214 protrudes from a central opening of the second annular portion 210toward the rotary electric machine system 10. The number of the legmembers 212 is appropriately set in accordance with a coupling strengthrequired between the gas turbine engine 200 and the rotary electricmachine system 10. Stated otherwise, the number of the leg members 212is not particularly limited to six as in the illustrated example.

Right ends of the leg members 212 are connected to both the secondannular portion 210 and the cylindrical cover member 214. In accordancewith this feature, support rigidity (support material strength) isimparted to the leg members 212. In addition, inlet openings of airbleed passages 216 are formed at locations where the leg members 212 areconnected with the cylindrical cover member 214. Further, as shown inFIG. 8 , the air bleed passages 216, which communicate with air bleedports 220 formed in a shroud case 218, are individually formed in theinterior of the leg members 212 and in the interior of the first annularportion 208. Outlet openings of the air bleed passages 216 areindividually formed on an end surface of the first annular portion 208on a side facing toward the second sub-housing 20. The outlet openingsoverlap with the collection flow path 74. More specifically, all of theplurality of air bleed passages 216 are in communication with thecollection flow path 74. In this manner, compressed air from theplurality of air bleed passages 216 flows into and is collected in thecollection flow path 74.

As shown in FIG. 8 , the gas turbine engine 200 is further equipped withthe shroud case 218, the compressor wheel 230, the turbine wheel 232, adiffuser 234, a combustor 236, and a nozzle 238, which are accommodatedin interior of the inner housing 202 and/or the outer housing 204.According to the present embodiment, the compressor wheel 230 and theturbine wheel 232 are separate members.

The shroud case 218 is a hollow body having a shape that issubstantially similar to that of the rectifying member 82, and is largerin comparison with the rectifying member 82. A small diameter left endthereof faces toward the rectifying member 82, and a large diameterright end thereof is inserted into the inner housing 202. A left end ofthe shroud case 218 is exposed to an air intake space 240 that is formedbetween the leg members 212 of the inner housing 202. The top portionwhich is on the right end of the rectifying member 82 is inserted intothe interior of the left end of the shroud case 218. Moreover, althoughthe shroud case 218 is gradually reduced in diameter from the right endtoward the left end thereof, a distal end of the left end is curved in amanner so as to expand outward in the diametrical direction.

The compressor wheel 230 is accommodated inside the shroud case 218.Stated otherwise, the shroud case 218 is disposed in surroundingrelation to the compressor wheel 230. However, the compressor wheel 230and the shroud case 218 are separated away from each other.

The compressor wheel 230 and the turbine wheel 232 are capable ofrotating together integrally with the rotating shaft 40. Morespecifically, as shown in detail in FIG. 5 , the compressor wheel 230includes a small diameter cylindrical portion 242 (hollow cylindricalportion) at a left end thereof. The small diameter cylindrical portion242 enters into the through hole 84 that is formed in the top portion ofthe rectifying member 82. On an inner wall of the small diametercylindrical portion 242, a first outer circumferential side spline 85(outer circumferential side engaging portion) is formed, which is madeup from a plurality of teeth that extend in a diametrical inwarddirection and are provided annularly. The first outer circumferentialside spline 85 enmeshes with the first inner circumferential side spline66 that is formed on the outer circumferential wall of the right openingend 42 b of the outer side shaft 36. Moreover, the outer side shaft 36is press-fitted into a hollow interior part of the small diametercylindrical portion 242. Therefore, the inner circumferential wall ofthe small diameter cylindrical portion 242, particularly the leftwardopening, presses the outer peripheral wall of the right opening end 42 bof the outer side shaft 36 inwardly. Due to being enmeshed andpress-fitted in the manner described above, the compressor wheel 230 isconnected to the outer side shaft 36 and hence to the rotating shaft 40.

At a diametrical center of the compressor wheel 230, a shaft hole 244 isformed that extends in the left-right direction. In such a shaft hole244, a second outer circumferential side spline 246 (outercircumferential side tooth portion), which is made up from a pluralityof teeth that extend in a diametrical inward direction and are providedannularly, is engraved on an inner wall in close proximity to the leftend. Further, a hole diameter at a location where the shaft hole 244 isconnected to the hollow interior part of the small diameter cylindricalportion 242 is set to be slightly smaller in comparison with otherlocations thereof. Therefore, an inner flange portion 248 is provided inthe vicinity of an opening on the side of the small diameter cylindricalportion 242 of the shaft hole 244 of the compressor wheel 230. The holediameter (diameter) of the shaft hole 244 is minimal at the site wherethe inner flange portion 248 is provided.

The output shaft 250 that is provided in the turbine wheel 232 isinserted into the shaft hole 244. The left distal end of the outputshaft 250 extends to substantially the same position as the left distalend of the small diameter cylindrical portion 242 of the compressorwheel 230. As noted previously, the outer circumferential wall of theright opening end 42 b of the outer side shaft 36 is inserted into thehollow interior part of the small diameter cylindrical portion 242.Therefore, the left end of the output shaft 250 that projects out fromthe shaft hole 244 enters into the shaft connecting hole 62 of therotating shaft 40. A male threaded portion 252 is engraved on the leftend of the output shaft 250, and the male threaded portion 252 isscrew-engaged with the female threaded portion 64 formed on the innerwall of the shaft connecting hole 62. Due to such screw-engagement, therotating shaft 40 and the output shaft 250 are connected.

A second inner circumferential side spline 254, which is an innercircumferential side tooth portion, is formed in the vicinity of theleft end of the output shaft 250. The second inner circumferential sidespline 254 enmeshes with the second outer circumferential side spline246 that is formed on the inner circumferential wall of the shaft hole244 of the compressor wheel 230. Further, a left end part of the outputshaft 250 is inserted through the inner flange portion 248 by way ofpress fitting.

As shown in FIG. 8 , a ring member 256, which is made up from aheat-resistant metal material such as a nickel based alloy or the like,is interposed between the compressor wheel 230 and the turbine wheel232. As shown in FIG. 9 , a fitting hole 258 which extends from thecompressor wheel 230 toward the turbine wheel 232 is formed in the ringmember 256. Further, a plurality of (for example, three) labyrinthconvex portions 264 are formed on the outer peripheral wall of the ringmember 256. The labyrinth convex portions 264, together with projectingin a diametrically outward direction of the ring member 256, encirclealong a circumferential direction of an outer circumferential wallthereof. As will be discussed later, back-flowing of a combusted fuel(exhaust gas) generated by the combustor 236 into the compressor wheel230 can be prevented by the labyrinth convex portions 264.

An annular protrusion 268 projects from a right end surface of thecompressor wheel 230 that faces toward the turbine wheel 232. When aleft end surface of the ring member 256 is seated on the right endsurface of the compressor wheel 230, the annular protrusion 268 isfitted into the fitting hole 258. On the other hand, the output shaft250 extends from a left end surface of the turbine wheel 232 that facestoward the compressor wheel 230. Further, on the left end surface, afitting protrusion 270 that encircles the output shaft 250 in asurrounding manner is formed to project from the turbine wheel 232. Whena right end surface of the ring member 256 is seated on the left endsurface of the turbine wheel 232, a top surface of the fittingprotrusion 270 is fitted into the fitting hole 258. In accordance withthe foregoing, each of respective parts of the compressor wheel 230 andthe turbine wheel 232 are fitted into the fitting hole 258. In such astate, the ring member 256 is sandwiched between both of the wheels 230and 232.

On the other hand, in the hollow interior of the outer housing 204 (seeFIG. 8 ), the labyrinth convex portions 264 are surrounded by anintermediate plate 266, together with being inserted inside a holeportion 272 that is formed in the intermediate plate 266. A labyrinthflow path is formed by an inner wall of the hole portion 272 and thelabyrinth convex portions 264 that abut against the inner wall. Thecompressed air generated by the compressor wheel 230 reaches thelabyrinth convex portions 264 via a back surface of the compressor wheel230. On the other hand, a combustion gas arrives at the labyrinth convexportions 264 from a turbine wheel 232 side. Since the pressure of thecompressed air is set to be higher than the pressure of the combustiongas, it is possible to prevent the combustion gas from passing throughthe labyrinth convex portions 264 and flowing inwardly to a compressorwheel 230 side.

As shown in FIG. 8 , in a hollow interior part of the outer housing 204,portions of the shroud case 218 and the compressor wheel 230 where thediameters thereof are maximal, and the intermediate plate 266 aresurrounded by the diffuser 234. Furthermore, the turbine wheel 232 issurrounded by the nozzle 238, and the nozzle 238 is surrounded by thecombustor 236. An annular combustion air flow passage 273 through whichcombustion air flows is formed between the combustor 236 and the outerhousing 204. On the other hand, a fuel supply nozzle 274 in order tosupply fuel to the combustor 236 is positioned and fixed on a right endsurface of the outer housing 204.

In this instance, relay holes 276 are formed in the combustor 236 forallowing the combustion air flow passage 273 to communicate with theinterior of the combustor 236. Further, non-illustrated fine pores forforming an air curtain to cool the interior of the combustor 236 areformed in the combustor 236. As will be discussed later, the combustionair that is compressed by the compressor wheel 230 reaches the interiorof the combustor 236 via the diffuser 234, the combustion air flowpassage 273, and the relay holes 276. Furthermore, a non-illustrateddelivery hole, which supplies to the turbine wheel 232 a fuel(hereinafter also referred to as a “combusted fuel,” wherein the term“combusted fuel” has the same meaning as the “combustion gas” or the“exhaust gas after combustion”) that is combusted together with thecombustion air, is formed in the nozzle 238 at a site surrounding thelargest diameter portion of the turbine wheel 232.

Further, a discharge port 280 provided with a non-illustrated dischargepipe for discharging the combusted fuel opens on a right end of theouter housing 204 and the nozzle 238. The combusted fuel passes throughthe delivery hole and progresses into the nozzle 238, and thereafter,the combusted fuel is expelled out of the outer housing 204 via thedischarge port 280 under the action of the rotating turbine wheel 232.

The combined power system 300 according to the present embodiment isconstructed basically as described above. Next, a description will begiven concerning operations and advantageous effects thereof.

In the present embodiment, the rotary electric machine system 10constitutes the combined power system 300 together with the gas turbineengine 200. Therefore, as shown in FIG. 5 , the output shaft 250 isconnected to the rotating shaft 40. In this instance, the shaftconnecting hole 62 is formed in the right end part 46 b of the innerside shaft 34 that makes up the rotating shaft 40, and the femalethreaded portion 64 is engraved on an inner circumferential wall of theshaft connecting hole 62. Further, the male threaded portion 252 isengraved on the left end of the output shaft 250. The left end isinserted into the shaft connecting hole 62, and the male threadedportion 252 is screw-engaged with the female threaded portion 64.

In this manner, since one end of the output shaft 250 is inserted intothe shaft connecting hole 62 that is formed at one end of the rotatingshaft 40, the length of the rotating shaft 40 and the output shaft 250after being connected to each other is smaller than the total length ofboth of the shafts 40 and 250. Further, from the fact that the outputshaft 250 is inserted into the shaft connecting hole 62 of the rotatingshaft 40, the diameter of the output shaft 250 is set to be smaller thanthe diameter of the shaft connecting hole 62. Accordingly, the outputshaft 250 is small and lightweight. Due to the above reasons, thecombined power system 300 can be made both small in scale andlightweight.

In addition, connection terminals of the battery 170 (see FIG. 7 ),which serves as an external power source, are connected with respect tothe U-phase terminal 156 a, the V-phase terminal 156 b, and the W-phaseterminal 156 c inside the terminal casing 22. In this state, a directcurrent is supplied from the battery 170. The conversion circuit 174 ofthe electrical current converter 172 shown in FIGS. 2 and 7 convertssuch a direct current into an alternating current, and supplies thealternating current to the electromagnetic coil 116 (the U-phase coil,the V-phase coil, and the W-phase coil) via the U-phase terminal 156 a,the V-phase terminal 156 b, and the W-phase terminal 156 c. By thealternating current flowing through the electromagnetic coil 116, analternating magnetic field is generated in the stator 32. Therefore,attractive forces and repulsive forces act alternately between theelectromagnetic coil 116 and the permanent magnets 88 of the rotor 30.As a result, the rotating shaft 40 begins to rotate. It is a matter ofcourse that the rotating shaft 40 may also be rotated by a widely-knowntype of starter (not shown).

In this instance, as shown in FIG. 5 , the first inner circumferentialside spline 66 is formed on the outer circumferential wall of the rightopening end 42 b of the outer side shaft 36 that constitutes therotating shaft 40, and further, the first outer circumferential sidespline 85 is formed on the inner wall of the small diameter cylindricalportion 242 of the compressor wheel 230. Additionally, the first innercircumferential side spline 66 and the first outer circumferential sidespline 85 enmesh with each other. Furthermore, the second innercircumferential side spline 254 is formed on the output shaft 250, andthe second outer circumferential side spline 246 is formed on the innerwall of the shaft hole 244 of the compressor wheel 230. Additionally,the second inner circumferential side spline 254 and the second outercircumferential side spline 246 enmesh with each other. Therefore, arotational torque of the rotating shaft 40 is rapidly transmitted to theoutput shaft 250 via the compressor wheel 230.

More specifically, when the rotating shaft 40 begins to rotate, theoutput shaft 250 also begins rotating integrally with the rotating shaft40. Accompanying such rotation, the compressor wheel 230 and the turbinewheel 232, which are supported by the output shaft 250, rotate togetherintegrally with the output shaft 250. As discussed previously, byproviding the first inner circumferential side spline 66 which serves asthe inner circumferential side engaging portion, the first outercircumferential side spline 85 which serves as the outer circumferentialside engaging portion, the second inner circumferential side spline 254which serves as the inner circumferential side tooth portion, and thesecond outer circumferential side spline 246 which serves as the outercircumferential side tooth portion, and by the first innercircumferential side spline 66 and the first outer circumferential sidespline 85, as well as the second inner circumferential side spline 254and the second outer circumferential side spline 246 being mutuallyenmeshed (placed in engagement) with each other, the rotational torqueof the rotating shaft 40 can be sufficiently transmitted to the outputshaft 250.

In addition, the right end part of the rotating shaft 40 is press-fittedinto the hollow interior part of the small diameter cylindrical portion242 of the compressor wheel 230, and the left end part of the outputshaft 250 is press-fitted into the inner flange portion 248 of thecompressor wheel 230. Therefore, the axis of the rotating shaft 40 andthe axis of the output shaft 250 accurately coincide with each other.Consequently, the output shaft 250 is sufficiently prevented fromrotating in eccentric manner or while being subjected to vibrations.

In addition, as shown in FIG. 9 , the ring member 256 is interposedbetween the compressor wheel 230 and the turbine wheel 232. The annularprotrusion 268 on the right end surface of the compressor wheel 230, andthe fitting protrusion 270 on the left end surface of the turbine wheel232 are fitted respectively into the fitting hole 258 of the ring member256. These fittings also contribute to suppressing eccentric rotation(and vibration) of the output shaft 250. Accordingly, there is no needto provide a mechanism for suppressing vibrations, or to make the outputshaft 250 large in diameter. Consequently, it is possible to reduce thesize and scale of the combined power system 300.

Furthermore, frictional forces are generated, respectively, between theright end surface of the compressor wheel 230 and the left end surfaceof the ring member 256, and between the right end surface of the ringmember 256 and the left end surface of the turbine wheel 232. Owing tosuch frictional forces, the compressor wheel 230, the ring member 256,and the turbine wheel 232 are in close contact with each other.Accordingly, it is possible to prevent both of the wheels 230 and 232from rotating.

Further still, when the combined power system 300 is assembled, thecompressor wheel 230 and the turbine wheel 232 are aligned (centered) bythe above-described fittings with respect to the output shaft 250. Ascan be understood from this feature, by the ring member 256 beingdisposed between both of the wheels 230 and 232, and the portions ofboth of the wheels 230 and 232 being individually fitted into thefitting hole 258 of the ring member 256, it becomes easy to center thecompressor wheel 230 and the turbine wheel 232 with respect to theoutput shaft 250.

In addition, due to the aforementioned rotation, as shown in FIG. 8 ,atmospheric air is drawn into the shroud case 218 from the air intakespace 240 provided between the leg members 212 of the inner housing 202.In this instance, the rectifying member 82 is located in the diametricalcenter of the inner housing 202. As discussed previously, the rectifyingmember 82 is of a chevron shape in a manner so as to be reduced indiameter toward the shroud case 218, and in addition, the sidecircumferential wall 83 is smooth. Therefore, the atmospheric air thatis drawn in is rectified by the rectifying member 82 so as to flowtoward the shroud case 218. Since the right end of the rectifying member82 enters from the left end opening of the shroud case 218, theatmospheric air efficiently enters into the shroud case 218. In thismanner, due to the fact that the rectifying member 82 is formed in theshape as described above, and the distal end thereof is made to enterinto the shroud case 218, the atmospheric air can be efficientlycollected in the shroud case 218.

The atmosphere air that is drawn into the shroud case 218 flows throughbetween the compressor wheel 230 and the shroud case 218. Since thespace between the compressor wheel 230 and the shroud case 218 issufficiently narrow in comparison with the leftward opening of theshroud case 218, the atmospheric air is compressed when flowingtherethrough. Stated otherwise, compressed air is generated.

The air bleed ports 220 are formed in the vicinity of the right end(base portion) of the shroud case 218. On the other hand, proximal endsof the leg members 212 of the inner housing 202 are positioned on theouter circumferential side of a substantially intermediate portion inthe lateral (left-right) direction of the shroud case 218. The inletopenings of the air bleed passages 216 are formed in the proximal ends.Therefore, a portion of the compressed air is diverted from the airbleed ports 220 as the curtain air, and proceeds to the secondsub-housing 20 through the air bleed passages 216 that are formed in theleg members 212. As shown in FIG. 6 , the curtain air flows into thecollection flow path 74 from the outlet openings of the air bleedpassages 216, and is collected and spread out in an annular shape. Thecurtain air further passes from the collection flow path 74 through theupstream side communication holes 76, and after having been distributedinto the relay communication passages 78, flows respectively from eachof the three individual downstream side communication holes 80 a to 80 cand through the hollow interior parts of the hollow pipe members 158 ato 158 c shown in FIG. 1 , etc.

The hollow pipe members 158 a to 158 c are positioned on the outercircumferential side of the cooling jacket 21. Accordingly, in theprocess of the curtain air flowing along the hollow pipe members 158 ato 158 c, the heat of the curtain air is sufficiently conducted to thecooling medium that was supplied beforehand to the cooling jacket 21.Consequently, the temperature of the curtain air becomes comparativelylow. More specifically, according to the present embodiment, thetemperature of the curtain air can be lowered by the cooling jacket 21which serves in order to cool the rotary electric machine 12 and theelectrical current converter 172. Therefore, in the gas turbine engine200 or the rotary electric machine system 10, there is no need toseparately provide cooling equipment in order to cool the curtain air.Consequently, by such an amount, it is possible to reduce the size andscale of the combined power system 300.

The curtain air flowing through the hollow pipe member 158 a flows intothe internal space of the measuring device casing 24, as shown in FIG. 2. Consequently, an air curtain is formed in the measuring device casing24. Surplus curtain air flows into the hollow interior (internal space)of the terminal casing 22 through the casing-to-casing communicationhole. An air curtain is formed inside the terminal casing 22 by suchsurplus curtain air, and by the curtain air that has flowed through thehollow pipe members 158 b and 158 c and into the internal space of theterminal casing 22.

As shown in FIG. 3 , the surplus curtain air inside the terminal casing22 flows into the accommodation chamber 114 that is formed in the mainhousing 16. In this instance, from the fact that the terminal casing 22and the measuring device casing 24 are disposed on the left side of themain housing 16, the curtain air flows inwardly from the left end of theaccommodation chamber 114. Thereafter, the curtain air initially entersinto the inner hole of the stator 32, and more specifically, intoclearances between the outer circumferential wall of the columnarprotrusion 96 and the insulating base members 118.

Thereafter, a portion of the curtain air flows toward a first shaftinsertion hole 98 side. Further, the remaining portion of the curtainair flows through the clearances between the outer walls of thepermanent magnets 88 and the inner wall of the electromagnetic coil 116,or in other words, toward the accommodation chamber 114, and toward aninsertion hole 68 side. In this manner, the curtain air branches into aportion that flows toward the first shaft insertion hole 98 at the leftend (the first end part), and a portion that flows toward the insertionhole 68 at the right end (the second end part). Moreover, as can beunderstood from the above description, concerning the flow passage forthe curtain air, the internal spaces of the terminal casing 22 and themeasuring device casing 24 define an upstream side thereof, and theaccommodation chamber 114 of the main housing 16 defines a downstreamside thereof.

The curtain air that has flowed to the first shaft insertion hole 98side passes through the first bearing 92 disposed inside the first shaftinsertion hole 98. On the other hand, the curtain air that has flowed tothe insertion hole 68 side passes through the second bearing 94 disposedinside the insertion hole 68. Thereafter, for example, both of suchcurtain airs in which the lubricating oil is contained pass through alubricating discharge path, and are discharged into an oil tank (neitherof which is shown), and the curtain airs are separated into thelubricating oil and the air. The lubricating oil is supplied again tothe first bearing 92 and the second bearing 94. On the other hand, theair is discharged, for example, into the atmosphere.

The compressed air that has passed between the shroud case 218 and thecompressor wheel 230 without entering into the air bleed ports 220becomes the combustion air, and as shown in FIG. 8 , proceeds into thediffuser 234. The combustion air flows out from an outlet hole formed ina wall portion of the diffuser 234, and into the combustion air flowpassage 273 formed between the combustor 236 and the outer housing 204.The combustion air further passes through the relay holes 276 and thefine holes formed in the combustor 236, and via a clearance or the likebetween the combustor 236 and the fuel supply nozzle 274, the combustionair enters into a hollow interior part, and more specifically, into acombustion chamber of the combustor 236.

The combustor 236 is in a preheated state, and further, the fuel issupplied from the fuel supply nozzle 274 into the hollow interior (thecombustion chamber) thereof. The fuel is combusted together with thecombustion air and becomes a high temperature combusted fuel. By thecombusted fuel that is supplied into the nozzle 238 from the deliveryhole undergoing expansion in the nozzle 238, the turbine wheel 232begins to rotate at a high speed. From the fact that the output shaft250 is provided on the turbine wheel 232 together with the compressorwheel 230 being externally fitted onto the output shaft 250,accompanying the high speed rotation of the turbine wheel 232, theoutput shaft 250 and the compressor wheel 230 rotate integrallytherewith at a high speed. Moreover, the combusted fuel is discharged tothe exterior of the outer housing 204 through a non-illustrateddischarge pipe provided in the discharge port 280.

The ring member 256 is interposed between the compressor wheel 230 andthe turbine wheel 232, and also fulfills a role as a sealing member forsealing a space between both of the wheels 230 and 232. In addition, asshown in FIG. 9 , the plurality of labyrinth convex portions 264 areformed on the outer circumferential wall of the ring member 256, and thelabyrinth convex portions 264 abut against an inner wall of the holeportion 272 that is formed in the intermediate plate 266 (refer to FIG.9 ). The compressed air generated by the compressor wheel 230 reachesthe labyrinth convex portions 264 via a back surface of the compressorwheel 230. Further, the combustion gas arrives at the labyrinth convexportions 264 from the turbine wheel 232 side. As noted previously, thepressure of the compressed air is set to be higher than the pressure ofthe combustion gas. Therefore, passing of the combustion gas through thelabyrinth convex portions 264 and flowing inwardly to the compressorwheel 230 side is suppressed. Due to the above reasons, a situation isavoided in which the combusted fuel, for example, enters into the shafthole 244 from between both of the wheels 230 and 232.

As shown in FIG. 8 , when the output shaft 250 begins to rotate at ahigh speed, supplying of the electrical current from the battery 170(see FIG. 7 ) to the electromagnetic coil 116 is stopped. However, sincethe turbine wheel 232 is rotated at a high speed by the combusted fuelas described above, in following relation with the rotation of theturbine wheel 232 and the output shaft 250 in an integrated manner, therotating shaft 40 also rotates integrally with the turbine wheel 232 andthe output shaft 250. At this time as well, for the same reasons asdescribed above, a sufficient rotational torque is transmitted from theoutput shaft 250 to the rotating shaft 40.

In addition, accompanying the rotation of the rotating shaft 40 alongwith the permanent magnets 88, an alternating current is generated inthe surrounding electromagnetic coil 116. The alternating current istransmitted to the electrical current converter 172 shown in FIGS. 2 and7 via the U-phase terminal 156 a, the V-phase terminal 156 b, and theW-phase terminal 156 c. The conversion circuit 174 of the electricalcurrent converter 172 converts such an alternating current into a directcurrent. When it is determined that the output of an external load (forexample, a motor) that is electrically connected to the battery 170 hasdecreased, the control circuit 178 of the electrical current converter172 transfers the direct current to the battery 170 through thecapacitor 176 (see FIG. 7 ). Consequently, the battery 170 is charged.

In this process, within the electrical current converter 172, inparticular, the conversion circuit 174 and the capacitor 176 becomeheated. However, according to the present embodiment, the equipment case180 is positioned and fixed to the outer circumferential wall of themain housing 16, and further, the conversion circuit 174 and thecapacitor 176 inside the equipment case 180 are placed in closeproximity to the cooling jacket 21. Therefore, the heat of theconversion circuit 174 and the capacitor 176 is rapidly conducted to thecooling medium inside the cooling jacket 21. Consequently, a situationis avoided in which the conversion circuit 174 and the capacitor 176become excessively high in heat.

Moreover, as shown in FIG. 3 , the direction in which the output shaft250 and the rotating shaft 40 are rotated is preferably a direction thatis opposite to the direction in which the small cap nut 58, the largecap nut 60, and the male threaded portion 252 are rotated whenscrew-engagement thereof is carried out. This is because, in this case,a situation is avoided in which the small cap nut 58, the large cap nut60, and the male threaded portion 252 become loosened during rotation ofthe rotating shaft 40. Moreover, the small cap nut 58, the large cap nut60, and the male threaded portion 252 may be provided in advance with amechanism for preventing loosening thereof.

In this instance, the lubricating oil is supplied in the form of a jetflow to the first bearing 92 and the second bearing 94 that rotatablysupport the rotating shaft 40 on the rotary electric machine housing 14.Owing to this feature, since the first bearing 92 and the second bearing94 are cooled by the lubricating oil, seizure can be prevented fromoccurring in the first bearing 92 and the second bearing 94. Moreover,as noted previously, in the rotary electric machine system 10, the flowpassages are formed in which the internal spaces of the terminal casing22 and the measuring device casing 24 are provided on the upstream side,and the first bearing 92 and the second bearing 94 are provided on thedownstream side. Further, a labyrinth sealing structure is provided inthe flow passage, and the curtain air flows through such a labyrinthsealing structure. Therefore, it is unlikely for the lubricating oil toenter into the internal spaces of the terminal casing 22 and themeasuring device casing 24.

Moreover, an air curtain made of curtain air is formed in the internalspaces of the terminal casing 22 and the measuring device casing 24.Accordingly, even if the lubricating oil enters into the internal spacesof the terminal casing 22 and the measuring device casing 24, adheringof the lubricating oil to the U-phase terminal 156 a, the V-phaseterminal 156 b, the W-phase terminal 156 c, the thermistor 152, and thelike is suppressed. For the aforementioned reasons, it is possible toeffectively avoid a situation in which the electric terminal portions towhich the battery 170 is electrically connected, the measuring device(the thermistor 152), and the like are contaminated with lubricatingoil.

In addition, in the rotary electric machine system 10, the curtain airthat has passed through the first bearing 92 and the second bearing 94flows therethrough in a manner so as to be discharged to the exterior ofthe rotary electric machine housing 14. Therefore, even if thelubricating oil leaks out from the first bearing 92 and the secondbearing 94, the lubricating oil is accompanied by the curtain air and isdischarged to the exterior of the rotary electric machine housing 14.Accordingly, it is possible to avoid a situation in which lubricatingoil that has leaked out proceeds toward a rotor 30 side or remainsinside the rotor 30.

Accompanying the rotation of the rotating shaft 40, the plurality of thepermanent magnets 88 retained on the large diameter portion of the outerside shaft 36 rotate. Consequently, an electrical current is induced inthe electromagnetic coil 116 (the U-phase coil, the V-phase coil, andthe W-phase coil) that face toward the permanent magnets 88. Theelectrical current is taken out via the U-phase terminal 156 a, theV-phase terminal 156 b, and the W-phase terminal 156 c as electricalpower for energizing an external device.

The electromagnetic coil 116 generates heat as the electrical currentflows therethrough. In this instance, the left end of the stator 32 isin contact with the curtain air prior to the curtain air branching off.Further, the curtain air, which flows along the longitudinal directionand passes through the accommodation chamber 114 toward the insertionhole 68, comes into contact with the outer wall and the inner wall ofthe stator 32. More specifically, a sufficient amount of the curtain aircomes into contact with respect to the left end of the stator 32, andthe curtain air after branching off comes into contact with the entiretyof the outer wall and the inner wall.

In addition, the cooling medium flows through the cooling jacket 21provided in the main housing 16. Due to the cooling medium, the stator32 including the electromagnetic coil 116 is rapidly, and hence therotary electric machine 12 is rapidly cooled by the curtain air and thecooling medium.

Further, the rotary electric machine housing 14 (the main housing 16) inwhich the rotary electric machine 12 is accommodated, and the terminalcasing 22 in which the U-phase terminal 156 a, the V-phase terminal 156b, and the W-phase terminal 156 c are accommodated are separatelyprovided. Therefore, it is unlikely for the influence of heat that isgenerated in the stator 32 inside the main housing 16 to be imparted tothe U-phase terminal 156 a, the V-phase terminal 156 b, and the W-phaseterminal 156 c inside the terminal casing 22. Moreover, from the factthat the terminals of the battery 170 (see FIG. 7 ) are electricallyconnected thereto, the U-phase terminal 156 a, the V-phase terminal 156b, and the W-phase terminal 156 c also generate heat. However, theU-phase terminal 156 a, the V-phase terminal 156 b, and the W-phaseterminal 156 c are rapidly cooled by the curtain air supplied to theterminal casing 22.

In the foregoing manner, the curtain air also serves in a dual manner tocool the heat generating locations in the rotary electric machine system10. In addition, from the fact that the electric terminal portions (theU-phase terminal 156 a, the V-phase terminal 156 b, and the W-phaseterminal 156 c), the electromagnetic coil 116, and the permanent magnets88 and the like are cooled, it is possible to avoid the influence ofheat on an output control or the like of the rotary electric machinesystem 10, and to avoid a situation in which excitation of theelectromagnetic coil 116 and the permanent magnets 88 decreases due toheat. As a result, the reliability of the rotary electric machine system10 is improved.

Further, from the fact that the main housing 16 in which the rotaryelectric machine 12 is accommodated, and the terminal casing 22 in whichthe U-phase terminal 156 a, the V-phase terminal 156 b, and the W-phaseterminal 156 c are accommodated are separately provided, the rotaryelectric machine 12 and the electric terminal portions are separatedaway from each other. Therefore, the U-phase terminal 156 a, the V-phaseterminal 156 b, and the W-phase terminal 156 c are not easily affectedby vibrations generated accompanying rotation of the rotor 30. Statedotherwise, the U-phase terminal 156 a, the V-phase terminal 156 b, andthe W-phase terminal 156 c are protected from such vibrations. Further,as discussed previously, in the first bearing 92 and the second bearing94, the occurrence of seizure is suppressed by the curtain air.Accordingly, the rotary electric machine system 10 is superior in termsof durability.

While the rotating shaft 40 is rotating, the angle of rotation (arotation parameter) of the rotating shaft 40 is detected by the resolver140. More specifically, the resolver rotor 56 which is externally fittedon the left end part 46 a of the inner side shaft 34 rotates togetherintegrally with the rotating shaft 40. Consequently, electric signalsgenerated in the resolver stator 130 are transmitted to the signalreceiver that is electrically connected to the signal receiver connector144. The signal receiver that has read the electric signals calculatesthe angle of rotation of the rotating shaft 40 based on the electricsignals, and transmits the result thereof to a non-illustrated controldevice or the like. The control device or the like obtains the RPM byway of a calculation based on the angle of rotation.

The resolver 140 is disposed on the protruding distal end 104 of therotating shaft 40 that is exposed from the rotary electric machinehousing 14. Accordingly, it is unlikely for the influence of heatgenerated in the electromagnetic coil 116 of the stator 32 inside therotary electric machine housing 14, and the influence of vibrationsgenerated accompanying rotation of the rotor 30 to be imparted to theresolver 140. In addition, the first bearing 92 and the second bearing94 that support the rotating shaft 40 are provided inside the rotaryelectric machine housing 14. Accordingly, vibrations of the firstbearing 92 and the second bearing 94 are suppressed by the rotaryelectric machine housing 14. This feature as well also makes it unlikelyfor the influence of vibrations to reach the resolver 140.

In the foregoing manner, by suppressing the transfer of heat andvibrations, the detection result of the rotation angle by the resolver140 becomes accurate. Further, the useful lifetime of the resolver 140is also lengthened.

For example, in the case that the resolver 140 is replaced with onehaving a larger inner diameter and outer diameter, the inner side shaft34 may be replaced with one having a larger diameter on the left endpart 46 a thereof. Moreover, in the case that a single solid rotatingshaft is adopted as the rotating shaft 40, in the case that such a solidrotating shaft is replaced with a large diameter one in order tocorrespond to the replacement of the resolver 140 with one having alarge inner diameter and outer diameter, it may be difficult for such asolid rotating shaft to pass through the first bearing 92 or the secondbearing 94. As can be understood from this situation, the rotating shaft40 of the present invention is constituted by the outer side shaft 36and the inner side shaft 34, together with the outer side shaft 36 beingpassed through the first bearing 92 and the second bearing 94. Further,the resolver rotor 56 is disposed on the portion of the inner side shaft34 that is exposed from the outer side shaft 36. Thus, by replacing theinner side shaft 34, it becomes possible to cope with resolvers 140having various inner diameters and outer diameters.

The present invention is not particularly limited to the above-describedembodiment, and various modifications can be adopted therein withoutdeparting from the essence and gist of the present invention.

For example, according to the present embodiment, the resolver 140 isadopted as the rotation parameter detector, however, it is also possiblefor a detector including a Hall element to be adopted.

Further, after the curtain air has been made to flow through theinternal space of the measuring device casing 24, the curtain air may beallowed to flow through the internal space of the terminal casing 22.Alternatively, the curtain air may be supplied separately to themeasuring device casing 24 and the terminal casing 22, and the curtainair that has flowed through the internal spaces of the casings 22 and 24may be distributed in a separate manner to the accommodation chamber114.

Furthermore, in the gas turbine engine 200, the compressor wheel 230 andthe turbine wheel 232 may be arranged in a reverse direction to thatshown in FIG. 8 . More specifically, the positions thereof may beexchanged with each other. In this case, the shaft hole 244 may beformed in the turbine wheel 232, and the output shaft 250 may beprovided in the compressor wheel 230. Apart therefrom, the types of thecompressor wheel 230 and the turbine wheel 232 may be of a centrifugaltype or an axial flow type. If the compressor wheel 230 and the turbinewheel 232 are arranged coaxially, a combination of a multi-stagecompressor wheel and a multi-stage turbine wheel may be used in whichthe centrifugal type and the axial flow type are combined.

Further still, as shown in FIG. 3 , the rotary electric machine 12constituting the rotary electric machine system 10 may be a motor inwhich the rotating shaft 40 is rotated by supplying electrical currentto the electromagnetic coil 116. In this case, the U-phase terminal 156a, the V-phase terminal 156 b, and the W-phase terminal 156 c areelectric terminal portions that receive electrical power from thebattery 170.

The electrical current converter may include a circuit for lowering orraising the voltage of an alternating current or a direct current.

Further, although in the above-described embodiment, an embodiment isillustrated in which the gas turbine engine 200 is used as a gas supplysource by partially diverting the compressed air generated by the gasturbine engine 200, as shown in FIG. 2 , it is also possible to use anexternally provided pump 290 as a gas supply source. In this case, theatmospheric air or the like may be compressed under the action of thepump 290, and may be supplied to the hollow pipe members 158 a to 158 cor the collection flow path 74. Moreover, in such a configuration, it isnot particularly necessary to divert the compressed air from the gasturbine engine 200.

In addition, the configuration for transmitting torque between therotating shaft 40 and the output shaft 250 is not particularly limitedto the meshing of splines. For example, one or more convex portions maybe provided on an outer circumferential wall of the rotating shaft 40 soas to project outwardly in a diametrical direction, whereas one or morerecessed portions may be formed on the output shaft 250, and the convexportions and the recessed portions may be engaged with each other.Alternatively, the rotating shaft 40 may have a polygonal shape, whereasa polygonal hole may be formed in the output shaft 250, and the rotatingshaft 40 may be engaged with such a polygonal hole. In the latter ofsuch elements, the outer circumferential wall of the rotating shaft 40becomes the inner circumferential side engaging portion, and the innercircumferential wall of the polygonal hole becomes the annular outercircumferential side engaging portion.

What is claimed is:
 1. A combined power system comprising: a rotaryelectric machine system including a rotary electric machine, and arotary electric machine housing in which a rotating shaft of the rotaryelectric machine is rotatably supported; and a gas turbine engineincluding an output shaft configured to support a turbine wheel and acompressor wheel and rotate integrally with the rotating shaft, and anengine housing in which the turbine wheel and the compressor wheel areaccommodated, the combined power system further comprising a terminalcasing disposed on an outer side wall of the rotary electric machinehousing and in which electric terminal portions are accommodated, theelectric terminal portions being configured to transmit and receiveelectrical power between the rotary electric machine and an externaldevice, wherein an air bleed port is formed in a shroud case thatsurrounds the compressor wheel, and compressed air that is compressed bythe compressor wheel flows into the air bleed port, an air bleed passageis formed in the engine housing, and the compressed air that has passedthrough the air bleed port flows through the air bleed passage, acooling jacket is provided for the rotary electric machine housing, acompressed air flow passage is formed on an outer circumferential sideof the cooling jacket, and the compressed air that has flowed throughthe air bleed passage flows through the compressed air flow passage, andthe terminal casing is disposed on a downstream side of the compressedair flow passage.
 2. The combined power system according to claim 1,further comprising a first bearing and a second bearing each configuredto rotatably support the rotating shaft in the rotary electric machinehousing, wherein a hollow interior part of the terminal casingcommunicates with a hollow interior part of the rotary electric machinehousing, and the compressed air that has passed through the compressedair flow passage is supplied to the first bearing and the secondbearing.
 3. The combined power system according to claim 2, wherein thefirst bearing and the second bearing are lubricated by a lubricatingoil.
 4. The combined power system according to claim 1, wherein thecompressed air flow passage comprises a plurality of compressed air flowpassages, and a distribution passage is formed in the rotary electricmachine housing in order to distribute the compressed air from the airbleed passage to the plurality of compressed air flow passages.
 5. Thecombined power system according to claim 4, wherein the air bleedpassage comprises a plurality of air bleed passages, and the compressedair that has flowed through the plurality of air bleed passages flowsinto the distribution passage.
 6. The combined power system according toclaim 5, wherein the distribution passage comprises one collection flowpath and a plurality of relay communication passages, the compressed airfrom the plurality of air bleed passages separately flows into thecollection flow path, and the plurality of relay communication passagesplace the collection flow path in communication with the plurality ofcompressed air flow passages separately.
 7. The combined power systemaccording to claim 6, wherein the collection flow path has an annularshape and the plurality of relay communication passages are disposed ina radial form.
 8. The combined power system according to claim 1,wherein the rotating shaft comprises an outer side shaft having a hollowcylindrical shape, and an inner side shaft a length of which is longerthan that of the outer side shaft, and which is configured to beremovably inserted inside the outer side shaft, one end part of theinner side shaft being exposed from the outer side shaft.